Excess flow cutoff valve with adjustable valve seat



Feb. 9, 1954 A. F. BARTOLAT EXCESS FLOW CUTOFF VALVE WITH ADJUSTABLE VALVE SEAT Filed April '7, 1951 Illllllll ff f5 ALBERT Fl BARTOLAT,

IN V EN TOR.

A TURA/EK Patented Feb. 9, 1954 UNITED EXCESS FLOW CUTOFF VALVE WITH ADJUSTABLE VALVE SEAT Albert F. Bartolat, Gardena, Calif. Application April 7, 1951, Serial N o. 219,805

8 Claims. (Cl. 137-498) This invention relates to fluid-dow, control devices and more particularly pertains to a flow regulating valve for use in fluid systems. While the principles involved are applicable to gaseous fluids, as well as liquids, the invention will be described herein for the purpose of disclosure as embodied in a valve for regulating the iiow of a liquid.

The invention is useful, for example, in installations where the primary requisite is to provide a normal rate of flow of a given magnitude, as in certain hydraulic systems and in systems for circulating, filtering, or feeding a liquid at a constant rate and/or pressure.

The preferred form of the invention is a compact valve structure that may be connected to the pipe or tubing of a system and after installation may be manually adjusted at will to maintain'selected rates of flow and/or selected pressures downstream from the valve notwithstanding wide fluctuations of pressure upstream from the valve.

A feature of the invention is that it may be used to advantage as means for protecting a system or a part of a system from damage by pressure surges. For example, such a device may be used to protect a filter unit that is of such character and construction as to be susceptible to damage by steep pressure rises. The present regulating valve automatically responds to sudden pressure rises by choking down flow and meets any excessive pressure surge by momentarily completely closing to cut off the system downstream from the valve.

In addition to these features it -is often desirable to provide in the same regulating device automatic prevention'of reverse ow in the event pressure upstream from the valve drops abnormally below the pressure downstream from the valve. The present flow regulator not only responds to predominance of upstream pressure in the manner heretofore described, but also functions as a check valve to close automatically in response to predominance of downstream pressure.

Finally, it is contemplated that the present valve will serve a further purpose in assuring continuous uninterrupted ow in systems where the fluid is of such character as to tend to clog regulating devices. Usually such clogging occurs inL a more or less accumulative manner under steady state conditions. To prevent such clogging, the present invention includes a movable wall member that is highly sensitive to small pressure changes and in thel course of its responsive action functions in a positive manner to dislodge any clogging material at critical points in the valve.

Broadly described, the regulating valve having these features incorporates a movable wall such as a piston to divide a valve chamber into an inlet portion and an outlet portion in a variable manner and relies upon this piston to control flow through the valve. The fact that flow through the valve depends upon the position of the piston makes it possible to adjustably control flow by adjustably controlling the position of the piston. While the piston is free to move in response to predominant pressure in either direction, it tends to seek an equilibriumposition and this equilibrium position can be adjustably varied.

The piston is free to move in one direction from its equilibrium position to cut off now in response to pressure surges upstream from the valve and is likewise free to move in the opposite direction to cut olf flow when the upstream pressure drops excessively below the downstream pressure.

In the preferred embodiment of the invention two valve actions are performed by the piston, one valve action controlling iiow past the piston from the inlet portion of the valve chamber to the outlet portion, and the other valve action controlling flow from the outlet portion of the valve chamber through the outlet port. This last valve action is provided by a valve seat together with a cooperating valve member carried ,by the piston. The valve seat is adjustable relative to the piston and its adjustment both limits the range of movement of the piston and determines the equilibrium position the piston will seek under given conditions.

The above and other features and advantages of the invention will be apparent in the detailed description to follow, taken with the accompanying drawings.

f In the drawings, which are to be regarded as merely illustrative,

Figure 1 is a longitudinal sectional view of the present preferred embodiment of the invention with some parts in side elevation, the piston being shown at one of its limit positions to cut oif reverse flow;

Figure 2 is a similar View showing the piston at an intermediate equilibrium position;

Figure 3 is a similar view showing the piston at its second limit position cutting off flow in' response to an excessively high pressure surge upstream from the valve; and V Figure 4 is a transverse section taken as' indicated by the line 4 4 of Figure 3. 1'

In the form of the invention shown in the drawings, the valve has a casing, generally designated I0, with a cylindrical wall II that forms a Valve chamber, generally designated I2. Threaded onto one end of the casing ID is a cap I3, having an inlet port I4 threaded for connection to pipe or tubing, the joint between the cap and the cylindrical wall II being sealed by a suitable gasket I5. At the other end of the casing is a thick transverse wall i6 having a transverse bore II and an intersecting longitudinal bore i8 forming an outlet passage to the chamber I2. The outer end of this passage is enlarged and threaded to provide an outlet port I9 adapted for connection to pipe or tubing.

A piston, generally designated 23, mounted in the valve chamber I2 in a freely slidable manner responds to pressure dierentials in either direction and, therefore, may be said to divide the valve chamber in a variable manner into an inlet" portion 2,4 and an outlet portion 25. It is contemplated that the pressure-responsive piston 2l)4 will operate a first valve means for controlling flow' from the inlet portion 24 of the valve chamber to the outlet portion 25 and will operate a second valve means for controlling flow from the outlet vportion`?` ofthe valve chamber through the outlet port I9. The arrangement is such that the piston progressively opens the first valve means as it progressively closes the second valve means and vice versa so that the piston tends to seekan equilibrium position at which both of the valvemeans are partially open. The two valve meansmay be constructed in various ways in various practices of the invention.

' In the construction shown in the drawing, the firstV valve means operated by the piston 2o is a passage from the inlet portion 24 of the valve chamber to the outlet portion 25, which passage isformedin part by the piston and in part by the cylindrical wall li 'of the valve chamber so thatthe ilow capacity of the passage depends upon the position of the piston. The passage has three parts, namely,' an angular inflow passage 30 the 'piston 2B extending from the upstream face`3I of the piston to the periphery of the piston, a circumferential passage in the form of a groove 32 around the inner circumference of the cylindrical Wall II, and an outow passage 33 extending through the piston from the piston periphery to the downstream face 34 of the piston. When the piston is in its rightward limit position, as'shown in Figure l, the two angular passagesfSD. and 33. of the piston are out of register with the circumferential groove 32 whereby cornmunication between the inlet portion 24 of the valve chamber and the outlet portion 25 is cut off. As the piston moves leftward, the two angular passages 30 and 33 of the piston move into partial registration with the circumferential groove 32, 'as shown in Figure 2, and the freedom for flow through the piston increases progressiveu ly as the vpiston approaches its leftward limit positionshownin Figure 3.

' To'provide the second valve means under control of the piston 20, a valve seat may be provided in the longitudinal bore I8 that constitutes part of the outflow passage leading to the outlet port I9 and preferably such a valve seat is arranged for adjustment relative to the piston 20. For this purpose a member 3.1 that maybe termed a valve stem extends through the longitudinal bore I8 into the outlet portion 25 of the valve chamber lz. This vaivestem 31 hasadnmetncai bore 38 in communication with the transverse bore 4 il of the valve casing and also has an intersect-v ing axial bore 3g that terminates in a valve seat 4E! facing the piston 20.

For axial adjustment, the valve stem 3l has an enlargement el in screw-thread engagement with a large bore 43 in the end of the valve casing I. Thus, manual rotation of the valve stem 3l' by means of a handle 44 on the outer end of the valve stern moves the valve seat 40 towards and away from the piston 20, the diametrical bore 38 of the valve stem remaining in communication with the transverse bore I'I of the valve casing throughout the range of adjustment of the valve seat. To prevent leakage around the valve stem 3l a suitable gland l5 may be threaded onto the end of the valve casing I0 to compress suitable packing '46 surrounding the valve stem.

The second valve means is completed by a valve member 5o carried by and preferably integral with the piston 2t, the valve member being for-med with a conical nose 5I to conform with the conical configuration of the valve seat 40. Seating of the valve member 5LB in the valve seat ci] reduces the crossesectional area of the piston that is subject to pressure in the outlet portion 25 of the valve chamber and thereby tends to set up a pressure differential to maintain the piston in its leftward limit position,A A suitable coil spring 52 is mounted in the outlet portion 25 of the valve chamber for continuous pressure against the downstream face 311 of the piston to compensate, at least in part, for any such prese sure differential and thereby tof at least reduce the tendency of the piston to. prolong the seating of the valve member 5B.

Under conditions of normal steady flow the piston hovers around an equilibriumL position, as indicated in Figure 2, or a narrow range of equilibrium positions with the two angular passages S and 33 of the piston in partial registration with the annular groove 32 and withthe nose of the valve member 56 spaced from, but relatively close to the valve seat dil. Further leftward movement of they piston, as viewed in Figure 2, would progressively restrict fluid flow out of the outlet portion 25 of the valve chamber and at the same time would progressivelyin-I crease the freedom of ilow through the piston into the outlet portion of the valve chamber,and the tendency of the piston to seek an equilibrium position may be undertsood from this fact.

It is also apparentthat adjustment ofthe valve seat il toward and away fromthe pistoni, by ro4 tation of the handle llltwould cause the piston to seek a new equilibrium position or range of vequine brium positions, outward adjustment of the valve seat shifting the equilibrium position to the left for increased flow-andinward adjustment shifting the equilibrium positioirto the right for reduced flow through the valve.

When the valve is constructed with. a transparent cylindrical wall II for the purpose of observation, the piston can be seen to. hover. or continually shift to slight degree. Such hovering may be the result of slightv pressureiluctuations in the pressure`- of the fluid suppliedto the valve, but there isv some reasony to believe thatV the hovering movement maybe inherent. inthe,A operf'- ation of the valve*y Thus, a certain minorK del,- gree of instability may arise frornrthe fact that the fluid streaming into the valve .scatto 'creates a pressure differential tending to force the valve member 5I)V further into the valve seat, which pressure differential isimmediately destroyed; the responsive movement of the piston causing h Vreduction offlow intothe valve seat. It may also be noted thatthe responsive movement'of the piston also increases the pressure of the spring v52. In any event, there is a marked tendency mediately shifts the highly responsive piston left- ,16

ward, as viewed in the drawings, to seat the valve member 50 in the valve seat 40 and thereby prevent transmission of the pressure rise through the valve. ',Ihus, the valve acts automatically to pre- @vent'destructiv pressurefrom reaching any part of the system downstream from the valve.

On the other hand, the piston, aided by the spring 52, responds quickly to a pressure differential in the opposite direction and promptly moves to the rightward limit position, shown in Figure 1, to prevent reverse flow through the valve. This last automatic action on the part of the valve may be useful to maintain pressure downstream from the valve in the event of pressure failure above the valve, and may prevent excessive loss of fluid from the system in the event a break occurs in the pipe or tubing upstream from the valve.

Preferably the valve is installed in a vertical position with the handle 44 at the top so that the weight of the piston as well as the force of the spring will urge the piston towards the position shown in Figure 1. In fact, with the valve in such a vertical position, the spring may be omitted in some installations.

My disclosure herein in specific detail of my preferred embodiment of the invention for the purpose of illustration will suggest to those skilled in the art various changes and modifications within the scope and spirit of my appended claims.

Having described my invention, I claim:

1. A flow regulating device of the character described, comprising: a valve casing forming a cylindrical valve chamber with an inlet port and an outlet port, said chamber having an inner recess between said ports; a piston in said chamber for movement between said ports across said recess, said piston having a passage from the inlet side of the piston to a peripheral point o f the piston and a passage from the outlet side of the piston to a second peripheral point of the piston spaced from the rst peripheral point, said peripheral points being positioned for simultaneous communication With said recess during the movement of the piston whereby the two passages and the recess constitute a flow passage between said two portions of the chamber with the flow capacity of the passage controlled by the position of the piston relative to said recess; yielding means urging said piston toward a position on the inlet side of said recess to cut off said flow passage; a valve responsive to said piston to cut off flow to said outlet port at a position of the piston at which said flow passage is open; and adjustable means for varying the position oi the piston at which said valve cuts off said outlet port.

2. A flow regulating device of the character described, comprising: a valve casing forming a cylindrical valve chamber with an inlet port and an outlet port, said chamber having an inner 'recessbetweensaidports; a'piston Vinisaid charnpiston toa second peripheral point ofthe piston spaced from the rst. peripheral point, saidperi'pheral.pointspbeing positioned for simultaneous communicationwith said vrecess during the movement of the piston wherebythe two passages and the recess constitute a-iiow passage between-said-two portions of vthechamber with `the ilow capacity ofthe passage controlled by the position of the piston relative to said recess; yielding means urging saidv piston toward a posiltion'on the inlet side offsaid recessto cut off said flowfpassage; a valveseat'in said outlet portionof the chamber throughv which fluid iiows ftol'said outlet port, saidvalve-:seat f'acing'f'said lpis`ton;i"a valve'member carriedl by the piston directed toward said seat to cooperate with said seat both for cutting off said outlet port and for stopping said piston at a limit position at which said ow passage is open; and means to vary the position of said valve seat thereby to vary said limit position of the piston.

3. A ow regulating device as set forth in claim 2 in which said valve seat is on the inner end of a threaded member having a portion exposed outside said chamber to permit manual adjustment thereof.

4. A flow regulating device of the character described, comprising: a valve casing forming a valve chamber having an inlet port and an outlet port; and a piston sliding in said chamber between said ports responsive to the exertion of uid pressure thereagainst and dividing the chamber into an inlet portion including said inlet port andan outlet portion including said outlet port, said piston having its periphery slidably contacting the wall of the chamber in each position to which the piston is slidably moved, said wall having a groove, the piston having an inow passage extending from said inlet portion to the periphery of the piston and an outflow passage extending from said periphery to said outlet portion of the valve chamber with the peripherally disposed ends of said passages arranged to be brought simultaneously into communication with said groove on sliding movement of the piston to a, predetermined position in the chamber, whereby to constitute, with said groove, a ow passage extending between said portions of the chamber.

5. A #flow regulating device as in claim 4, wherein said groove is extended circumferentially of the chamber and lies in a plane normal to the line of sliding movement of the piston, with said peripherally disposed ends of the passages being arranged in a common plane registering with the first-named plane in said predetermined position of the piston.

6. A iiow regulating device as in claim 5, wherein said passages and groove are proportioned to remain in communication both when in full and in partial register, whereby to vary the cross-sectional area of the iiow passage responsive to movement of the piston away from said predetermined position thereof.

7. A flow regulating device as in claim 5, wherein said groove is of greater width than the piston passages, whereby to retain the groove and piston passages in full register, on deviation of the piston from said predetermined position thereof occasioned by predetermined variations in pressure exerted thereagainst.

MQASB described, comprising: a valve easing forming a valve chamber having an inlet port, and im @utloi port.; a pigton sliding in Said ehambor homo@ said ports responsive to the exertion or iiuid med.- sure thereegainst and dividing thoohomber mio inlet and outlet; portions inolodiiis, respectively. the inlet and outlet ports said piston having it periphery slidably ooniaoting the woll of the chamber in each position to which. the :liaison s lidebly moved. said wail having o oiroumoroiitial groove, the piston having an inflow passage extending from the inlet; portion of the ohonibor to the periphery of the piston and an eiitow Daosage extending from said ooripherx to said outlet portion with the poripheroiiy dioposod oxido of said passages heine brought into ziimulionooos communication with said groom sin sliding movemont of the piston to a predetorminod position in the chamber to form a. now passage oxtondizig ooiwoen oaid inlet ond ouiloi 'poiiioiisi o valve seat in tho outlet; oor-tion oi tho @hamer 'ihiolih which iiuid owo to ille outlet mit. said dem, io@- ing the pieton: and a valve member tho piston dirooied toward odio Seat. s oid mision posads beine shifted out, of full, register with Said groove ori movement of iii@ piston o direotion away from aid. soot, wheroloy to inoreaso the .flowoopooiiv oi ooid sedi in dires@ relation. i0 on ottomidiit decrease in. the oapooiiy of., said flow pooo@ ALBERT F. BARTQLAT,

References cited the file of this potent UNITED STATES PATENTS Number Name Date 895,387 Ford Jan. 1, 1889 igasiv Amberg Mey 31i 1,932 2,4468960 cese V V T Mey 3, 1949 Branson ..Y Feb'. 5, 1952 

